EP2044294B1 - Turbocompresseur à double soupape de décharge - Google Patents

Turbocompresseur à double soupape de décharge Download PDF

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Publication number
EP2044294B1
EP2044294B1 EP20070733030 EP07733030A EP2044294B1 EP 2044294 B1 EP2044294 B1 EP 2044294B1 EP 20070733030 EP20070733030 EP 20070733030 EP 07733030 A EP07733030 A EP 07733030A EP 2044294 B1 EP2044294 B1 EP 2044294B1
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EP
European Patent Office
Prior art keywords
valve
wastegate
shaft
assembly according
valve assembly
Prior art date
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Active
Application number
EP20070733030
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German (de)
English (en)
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EP2044294A2 (fr
Inventor
Jim Mcewan
Lee Robinson
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Cummins Turbo Technologies Ltd
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Cummins Turbo Technologies Ltd
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Publication date
Application filed by Cummins Turbo Technologies Ltd filed Critical Cummins Turbo Technologies Ltd
Publication of EP2044294A2 publication Critical patent/EP2044294A2/fr
Application granted granted Critical
Publication of EP2044294B1 publication Critical patent/EP2044294B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
    • F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/105—Final actuators by passing part of the fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
    • F02B37/025—Multiple scrolls or multiple gas passages guiding the gas to the pump drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • F02B37/183—Arrangements of bypass valves or actuators therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87265—Dividing into parallel flow paths with recombining
    • Y10T137/8741—With common operator
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87265—Dividing into parallel flow paths with recombining
    • Y10T137/8741—With common operator
    • Y10T137/87442—Rotary valve
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87571—Multiple inlet with single outlet
    • Y10T137/87676—With flow control
    • Y10T137/87684—Valve in each inlet
    • Y10T137/87692—With common valve operator

Definitions

  • the present invention relates to a wastegated turbocharger.
  • the invention relates to a dual wastegate port and valve assembly for a turbocharger provided with a divided inlet turbine.
  • Turbochargers are well known devices for supplying air to the intake of an internal combustion engine at pressures above atmospheric pressure (boost pressures).
  • a conventional turbocharger essentially comprises an exhaust gas driven turbine wheel mounted on a rotatable shaft within a turbine housing connected downstream of an engine outlet manifold. Rotation of the turbine wheel rotates a compressor wheel mounted on the other end of the shaft within a compressor housing. The compressor wheel delivers compressed air to the engine intake manifold.
  • the turbocharger shaft is conventionally supported by journal and thrust bearings, including appropriate lubricating systems, located within a central bearing housing connected between the turbine and compressor wheel housings.
  • the turbine stage comprises a turbine chamber within which the turbine wheel is mounted.
  • An annular inlet passageway is defined between facing radial walls arranged around the turbine chamber.
  • An inlet volute is arranged around the inlet passageway and an outlet passageway extends from the turbine chamber.
  • the passageways and chambers communicate such that pressurised exhaust gas admitted to the inlet chamber flows through the inlet passageway to the outlet passageway via the turbine and rotates the turbine wheel.
  • vanes referred to as nozzle vanes
  • Turbines may be of a fixed or variable geometry type.
  • Variable geometry turbines differ from fixed geometry turbines in that the size of the inlet passageway can be varied to optimise gas flow velocities over a range of mass flow rates so that the power output of the turbine can be varied to suite varying engine demands. For instance, when the volume of exhaust gas being delivered to the turbine is relatively low, the velocity of the gas reaching the turbine wheel is maintained at a level which ensures efficient turbine operation by reducing the size of the annular inlet passageway.
  • Turbochargers provided with a variable geometry turbine are referred to as variable geometry turbochargers.
  • a turbocharger turbine may be provided with a valve controlled bypass port referred to as a wastegate, to enable control of the turbocharger boost pressure and/or shaft speed.
  • a wastegate valve (typically a poppet type valve) is controlled to open the wastegate port when the pressure of the boost air increases toward a pre-determined level, thus allowing some of the exhaust gas to bypass the turbine wheel.
  • the wastegate port opens into a bypass passageway which diverts the bypass gas flow to the turbine outlet or vents it to atmosphere.
  • the wastegate valve may be actuated by a variety of means, including electric actuators, but is more typically actuated by a pneumatic actuator operated by boost pressure delivered by the compressor wheel.
  • Turbochargers intended for installation on an engine with two banks of cylinders may be provided with a turbine which has a divided inlet volute. This provides separate parallel gas inlet flow paths to the turbine wheel from each of the engine cylinder banks so that separate impulses of the exhaust gases will be more effectively transmitted to the turbine wheel. Wastegating of such a divided inlet turbine requires two wastegate ports, one for each separate inlet path, controlled by a dual wastegate valve mechanism.
  • each valve member is loosely coupled to the support member by a pin which allows some movement of the valve member relative to the support member. This freedom of movement accommodates minor distortion in the support member. However, excessive freedom of movement between each valve member and the support member can result in premature opening of one or other valve member before the boost pressure reaches the predetermined level.
  • a dual wastegate valve mechanism proposed to further improve upon the mechanisms described above is disclosed in US Patent 5,046,317 .
  • a pair of wastegate valve members poppets
  • the support member is pivotally connected to a support arm at a mid point between the two valve members to allow a small degree of pivoting movement of the support member itself relative to the wastegate ports.
  • the combined freedom of movement of the valve members on the support member, and the support member on the support arm is said to accommodate differences in the valve seat height whilst ensuring each valve member firmly sits properly on its valve seat when the wastegate ports are closed.
  • the reaction forces exerted on the valve members have a component in the axial direction of the shaft which by virtue of the freedom of movement of the shaft in the axial direction provides a centering action.
  • the valve seats preferably incline at an angle greater than 90° (included angle).
  • Each valve seat is preferably equidistant from a line of intersection of the respective valve seat planes, but alternatively one valve seat may be closer to said line of intersection than the other.
  • the axial direction of the shaft preferably extends in a direction parallel to a plane containing a line joining the centres of the two valve seats, and in the case of valve seats equidistant from the line of intersection of the respective planes it is preferably parallel to a line joining the centres of the two valve seats.
  • the valve seats may be off set relative to the axis, so that one valve seat is closer to the axis than the other.
  • valve members are preferably loosely secured to the support shaft to enable a certain degree of freedom of movement of each valve member to improve seating.
  • the valve members may be rigidly secured to the shaft (or more preferably a support portion extending laterally from the shaft).
  • FIG. 1 this illustrates a turbocharger provided with a divide turbine inlet and twin wastegate valve assembly as disclosed in US 5,046,317 referred to above.
  • the illustrated turbocharger comprises a turbine 1 and a compressor 2 interconnected by a central bearing housing 3.
  • the turbine 1 comprises a turbine wheel 4 mounted on one end of a turbo shaft 5 within a turbine housing 6.
  • the compressor 2 comprises a compressor wheel 7 mounted on the other end of the turbo shaft 5 within a compressor housing 8.
  • the turbo shaft 5 rotates about the turbocharger axis on bearing assemblies (not shown) located within the bearing housing 3.
  • the turbine housing defines a divided inlet volute having parallel exhaust gas inlet paths 9 and 10 which deliver exhaust gas to the turbine wheel 4 via an annular inlet passage 11 and exits the turbine housing via an axial outlet passage 12.
  • the compressor housing 2 defines an axial inlet 13 and an outlet volute 14.
  • the turbine 1 is a wastegated turbine and as such each exhaust gas inlet path 9 and 10 is provided with a respective wastegate port 15 and 16 which communicate with a bypass gas passage 17 via a dual wastegate valve assembly.
  • the dual wastegate valve assembly comprises a pair of wastegate valve members, i.e. poppets 18 and 19 loosely mounted to opposite ends of a linking support member 20. Each poppet has a limited freedom of movement allowing the precise position of each poppet to shift slightly to accommodate small variations in the height of the respective valve seats defined around the opening of each outlet bypass port 9,10.
  • the support member 20 is mounted to one end of the support arm 21 which extends through a wall 22 of the turbine housing and is connected at its opposite end to an actuator arm 23.
  • a bushing 24 is provided in the turbine housing wall 22 to accommodate rotation of the support arm 21.
  • the end of the support arm 21 which is fixed to the support member 20 is bent at right angles to the axis of rotation of the support arm 21.
  • the opposite end of the support arm 21 is linked to the actuator arm 25 so that reciprocal movement of the actuator arm (as indicated by arrow 25) causes rotation of the support arm 21 which in turn moves the linking support member 20 and the poppets 18,19 to simultaneously open or close the wastegate ports 9,10.
  • the tip of the support arm 21 is secured to the support member 20 so as to allow limited angular movement between the two.
  • the pivotal connection between the tip of the support arm 21 and the support member 20 is intended to provide a centering action to improve accurate seating of the poppets.
  • the wastegate valve assembly is controlled to open as boost pressure produced by the compressor 2 reaches a predetermined level to permit a portion of exhaust gas flowing through the turbine inlet paths 9 and 10 to bypass the turbine wheel 4 and thus limit any further increase in boost pressure produced by the compressor.
  • the bypass gas passage 17 may communicate to atmosphere (as suggested in US 5,046,317 ) or may for instance communicate with the turbine outlet passage 12 so that the bypass gas flow merges with the main exhaust gas flow downstream of the turbine wheel 4.
  • FIGS 2 and 3 illustrate a dual wastegate port and valve assembly according to the present invention. Only those details relevant to the invention are described. For instance, other details of the turbocharger, such as the construction of the turbine housing and the parallel exhaust gas inlet paths, and the manner in which the wastegate ports communicate with the inlet paths, may be entirely conventional and could for instance have the general structure illustrated in Figure 1 .
  • FIG 2 is a perspective section through part of a turbocharger turbine housing illustrating dual wastegate ports 30 and 31 extending through a housing wall 32 and a dual wastegate valve assembly 33 according to the present invention.
  • Figure 3 is a view in the direction of arrow A in Figure 2 . It will be understood that the wastegate ports 30 and 31 communicate with respective exhaust gas flow paths (not shown) of a divided turbine inlet (not shown) which may for instance have substantially the same structure as that shown in Figure 1 .
  • the wastegate port 30 opens at a first surface 34 of the turbine wall 32 and the wastegate port 31 opens at a second surface 35 of a turbine wall 32.
  • the second wall surface 35 is inclined toward the first surface 34 forming a shallow V shape.
  • respective valve seats defined on surfaces 34 and 35 around the opening of each wastegate port 30,31 are preferably similarly inclined toward each other so that the plane of one valve seat meets the plane of the other valve seat at a line substantially equispaced between the centres of the openings of the wastegate ports 31,32.
  • the wastegate valve assembly 33 comprises a pair of wastegate valve members, in this case poppets 36 and 37, fixed to a valve member support 38 mounted on one end of a valve shaft 39 for rotation therewith.
  • the valve shaft 39 extends along an axis 40 which is preferably parallel to, but laterally offset from, a line joining the centres of the openings of each valve port 30 and 31.
  • the shaft 39 is supported for rotation about the axis 40 by a bushing 41 fitted in a bore through a housing wall portion 42.
  • a radially extending lever arm 43 is secured to the end of the shaft 39 opposite the valve member support 38.
  • the valve member support 38 comprises a sleeve portion 44 securely fixed to the shaft 39 and a flag portion 45 extending laterally from the sleeve 44.
  • Each valve member 36, 37 is secured to the support member flag portion 45 so that its sealing surface 36a, 37a lies in a plane parallel to the plane of the respective wastegate port valve seat.
  • the valve members 36 and 37 are preferably "loosely" secured to the support member 38, to allow a limited freedom of movement about an axis perpendicular to the plane of the respective valve seat, for instance to accommodate minor distortions in the valve member support 38 relative to the surfaces 34 and 35 of the housing wall 32. In the illustrated embodiment this is achieved by loosely riveting each valve member to the support member 38 in a conventional manner.
  • the shaft 39 is axially slidable within the bushing 41, and has a freedom of movement in the axial direction limited by the abutment of the sleeve 44 and bushing 41 on one side of the wall member 42, and the lever arm 43 and the bushing 41 on the opposite side of the wall member 42.
  • a wastegate valve actuator (not shown) is linked to the lever arm 43 in order to reciprocate the lever arm 43 through a small angle to rotate the shaft 39 sufficiently to open and close the wastegate ports 30 and 31.
  • the actuator may be a conventional pneumatic actuator linked to the lever arm 43 by an actuating arm (not shown) which reciprocates in response to pressure in the turbine compressor.
  • the actuator will be spring biased to maintain the wastegate valve in a closed position unless the spring bias is overcome by boost pressure transmitted to the actuator thus causing the wastegate valve to open.
  • other forms of actuator such as electric actuators controlled in accordance with monitored boost pressure, could also be used.
  • Actuating force applied to the lever arm in a anti-clockwise direction as shown in Figure 2 will close the wastegate ports 30 and 31 by seating the valve members 36 and 37 on respective housing surfaces 34 and 35.
  • the loose connection of the valve members 36 and 37 to the valve member support 38 will allow each valve member to shift slightly to accommodate minor deformation or wear in the valve or support 38 seats.
  • the combination of the inclined valve seats and the freedom of the shaft to move along its axis will tend to center the valve members on their valve seats as force is applied to maintain the valve members in a closed position.
  • the present invention therefore provides a dual wastegate port and valve assembly which provides for accurate seating of each valve member using a mechanically simple and robust mechanism.
  • Figures 4 and 5 illustrate a second embodiment of the present invention.
  • Figure 4 is a perspective view from above and Figure 5 is a sectional view, of a part of the turbine housing 50 defining dual wastegate ports 51 and 52 communicating between respective exchange gas inlet paths 53 and 54 and a bypass passage 55.
  • a dual wastegate valve assembly comprising valve members 56 and 57 seated on inclined wastegate port valves seats 58, 59 defined by bosses 60 and 61.
  • the valve seats 58 and 59 defined by the bosses 60 and 61 respectively, lie in preferably mutually inclined planes.
  • the valve members 56 and 57 are mounted to a valve member support 62 so that their sealing surfaces 63 and 64 lie (with some limited freedom and movement) in mutually inclined planes parallel to the valve seat planes.
  • valve member support 62 is mounted for rotation on one end of a shaft 69 and operates in the manner described in relation to the embodiment of Figures 3 and 4 .
  • valve member support links the two valve members and has angled portions to which each valve member is mounted.
  • each valve member could be mounted to a respective support arm extending from the sleeve portion rather than being directly linked.
  • valve seats defined at the opening of each wastegate port are inclined toward one another.
  • valve seats may be inclined away from one another in an inverted V shape.
  • orientation of the wastegate ports in the illustrated examples is perpendicular to each of the valve seats. This need not necessarily be the case, rather the wastegate ports may be angled with respect to the respective valve seats. Other modifications will be apparent to the appropriately skilled person.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Supercharger (AREA)

Claims (14)

  1. Ensemble de soupape de décharge (33) de turbocompresseur comprenant:
    un premier orifice de dérivation (30) communiquant avec une première partie d'une entrée d'échappement;
    un premier élément de soupape (36) conçu pour entrer en contact avec un premier siège de soupape entourant le premier orifice de dérivation et pour le rendre étanche;
    un second orifice de dérivation (31) communiquant avec une seconde partie d'une entrée d'échappement;
    un second élément de soupape (37) conçu pour entrer en contact avec un second siège de soupape entourant le second orifice et pour le rendre étanche;
    un arbre (39) supportant chaque élément de soupape (36, 37) d'une manière permettant une rotation autour d'un axe d'arbre (40) pour soulever les premier et second éléments de soupape (36, 37) tous les deux et rompre leur contact étanche avec les premier et second sièges de soupape, respectivement;
    caractérisé par le fait que le premier siège de soupape est incliné par rapport au second siège de soupape et l'arbre (39) a une liberté de mouvement dans la direction axiale (40).
  2. Ensemble de soupape de décharge selon la revendication 1, dans lequel le premier siège de soupape est situé dans un premier plan (34) et le second siège de soupape est situé dans un second plan (35), les premier et second plans étant inclinés l'un vers l'autre pour former un V.
  3. Ensemble de soupape de décharge selon la revendication 1, dans lequel le premier siège de soupape est situé dans un premier plan (34) et le second siège de soupape est situé dans un second plan (35), les premier et second plans s'éloignant l'un de l'autre en s'inclinant pour former un V inversé.
  4. Ensemble de soupape de décharge selon la revendication 2 ou la revendication 3, dans lequel ledit axe (40) s'étend dans une direction sensiblement orthogonale à la direction de la ligne d'intersection des premier et second plans (34, 35) et ledit axe (40) s'étend de manière sensiblement parallèle à une ligne de jonction des centres de chaque orifice de dérivation (30, 31).
  5. Ensemble de soupape de décharge selon l'une quelconque des revendications 2 à 4, dans lequel les sièges de soupape sont situés à égale distance de la ligne d'intersection des premier et second plans (34, 35).
  6. Ensemble de soupape de décharge selon l'une quelconque des revendications 2 à 4, dans lequel un siège de soupape est situé plus près de la ligne d'intersection des premier et second plans (34, 35) que l'autre siège de soupape.
  7. Ensemble de soupape de décharge selon l'une quelconque des revendications 1 à 6, dans lequel ledit axe (40) s'étend de manière sensiblement parallèle à un plan contenant une ligne de jonction des centres de chaque orifice de dérivation (30, 31).
  8. Ensemble de soupape de décharge selon l'une quelconque des revendications 1 à 6, dans lequel les premiers orifice de soupape (30) et élément de soupape (36) sont plus éloignés de l'axe (40) de l'arbre (39) que les seconds orifice de soupape (31) et élément de soupape (37).
  9. Ensemble de soupape de décharge selon l'une quelconque des revendications précédentes, dans lequel chaque élément de soupape (36, 37) est fixé à une partie de support (38) s'étendant latéralement par rapport audit arbre (39).
  10. Ensemble de soupape de décharge selon la revendication 9, dans lequel chaque élément de soupape (36, 37) est monté avec jeu sur l'élément de support (38) de manière à avoir une liberté de mouvement limitée.
  11. Ensemble de soupape de décharge selon la revendication 9 ou 10, dans lequel chaque élément de soupape (36, 37) est monté sur un support commun (38).
  12. Ensemble de soupape de décharge selon l'une quelconque des revendications précédentes, dans lequel ledit arbre (39) s'étend à travers une douille (41) supportée dans un alésage traversant une paroi (42), la liberté de mouvement de l'arbre (39) le long de son axe (40) étant limitée par des formations de butée définies par ou fixées sur des parties de l'arbre (39) sur les côtés axiaux respectifs de la douille (41).
  13. Ensemble de soupape de décharge selon la revendication 11, dans lequel une formation de butée est définie par un bras de levier (43) relié à une extrémité de l'arbre (39) pour assurer la rotation de celui-ci et l'autre formation de butée est définie par une partie d'un élément de support (38) prévu pour supporter lesdits éléments de soupape (36, 37) sur ledit arbre (39).
  14. Turbocompresseur incluant une turbine comprenant un passage d'entrée de gaz d'échappement divisé en une première partie et une seconde partie, comprenant, en outre, un ensemble de soupape de décharge (33) selon l'une quelconque des revendications précédentes.
EP20070733030 2006-05-31 2007-05-31 Turbocompresseur à double soupape de décharge Active EP2044294B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0610691A GB0610691D0 (en) 2006-05-31 2006-05-31 Turbocharger with dual wastegate
PCT/GB2007/002014 WO2007138325A2 (fr) 2006-05-31 2007-05-31 Turbocompresseur à double soupape de décharge

Publications (2)

Publication Number Publication Date
EP2044294A2 EP2044294A2 (fr) 2009-04-08
EP2044294B1 true EP2044294B1 (fr) 2014-08-13

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EP20070733030 Active EP2044294B1 (fr) 2006-05-31 2007-05-31 Turbocompresseur à double soupape de décharge

Country Status (7)

Country Link
US (1) US8336309B2 (fr)
EP (1) EP2044294B1 (fr)
JP (1) JP4987971B2 (fr)
CN (1) CN101460710B (fr)
BR (1) BRPI0712745A2 (fr)
GB (1) GB0610691D0 (fr)
WO (1) WO2007138325A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11634998B2 (en) 2018-10-08 2023-04-25 Borgwarner Inc. Wastegate assembly for use in a turbocharger and system including the same

Families Citing this family (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB0610691D0 (en) 2006-05-31 2006-07-12 Cummins Turbo Technologies Turbocharger with dual wastegate
CN102414419B (zh) * 2009-05-18 2014-04-23 博格华纳公司 涡轮增压器
CN101598038B (zh) * 2009-07-03 2012-05-09 康跃科技股份有限公司 涡轮增压器双层流道变截面涡轮机
JP2011144762A (ja) * 2010-01-15 2011-07-28 Mitsubishi Heavy Ind Ltd ウエストゲートバルブ
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CN101460710B (zh) 2013-07-17
JP4987971B2 (ja) 2012-08-01
WO2007138325A2 (fr) 2007-12-06
BRPI0712745A2 (pt) 2012-09-11
GB0610691D0 (en) 2006-07-12
US8336309B2 (en) 2012-12-25
CN101460710A (zh) 2009-06-17
JP2009539018A (ja) 2009-11-12
WO2007138325A3 (fr) 2008-01-17
US20090151352A1 (en) 2009-06-18
EP2044294A2 (fr) 2009-04-08

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